WO2010094786A2 - Élément de construction plat à amortissement des vibrations - Google Patents

Élément de construction plat à amortissement des vibrations Download PDF

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Publication number
WO2010094786A2
WO2010094786A2 PCT/EP2010/052166 EP2010052166W WO2010094786A2 WO 2010094786 A2 WO2010094786 A2 WO 2010094786A2 EP 2010052166 W EP2010052166 W EP 2010052166W WO 2010094786 A2 WO2010094786 A2 WO 2010094786A2
Authority
WO
WIPO (PCT)
Prior art keywords
bead
component
component according
piezoactuator
piezoelectric actuator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2010/052166
Other languages
German (de)
English (en)
Other versions
WO2010094786A3 (fr
Inventor
Christoph Fankhauser
Michael Vorraber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Magna Steyr Fahrzeugtechnik GmbH and Co KG
Original Assignee
Steyr Daimler Puch Fahrzeugtechnik AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Steyr Daimler Puch Fahrzeugtechnik AG and Co KG filed Critical Steyr Daimler Puch Fahrzeugtechnik AG and Co KG
Priority to US13/201,985 priority Critical patent/US9366310B2/en
Priority to DE112010000734.9T priority patent/DE112010000734B4/de
Priority to CN201080008049.1A priority patent/CN102317643B/zh
Publication of WO2010094786A2 publication Critical patent/WO2010094786A2/fr
Publication of WO2010094786A3 publication Critical patent/WO2010094786A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/005—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion using electro- or magnetostrictive actuation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2224/00—Materials; Material properties
    • F16F2224/02—Materials; Material properties solids
    • F16F2224/0283—Materials; Material properties solids piezoelectric; electro- or magnetostrictive

Definitions

  • the present invention relates to a planar component, in particular sheet metal element, which is provided with at least one piezoelectric actuator for its active vibration damping.
  • piezoactuators for feeding vibration-canceling structure-borne noise into a mechanical structure is known, for example, from US Pat. No. 4,626,730, EP 0 720 144 or WO 97/16048.
  • the piezoactuators are operated in a control loop with vibration sensors which are located at locations of maximum vibration amplitude in order to provide an actual value for the regulation goal of vibration minimization.
  • the known systems are currently not concerned with the optimization of the coupling of the piezoelectric noise into the component with regard to maximum damping of different vibration modes of the component.
  • the invention sets itself the goal of solving this problem.
  • the invention provides a sheet-like component, in particular sheet metal element, which is provided with at least one piezoelectric actuator for its active vibration damping and is characterized in that the piezoactuator is applied to the inside or outside of a bead formed in the component.
  • the depth of the bead can be reduced without impairing the mechanical strength, whereby the starting material and / or working steps during beading ("drawing") can be saved.
  • the component is for damping its fundamental modes with at least one bead per fundamental mode provided which causes its mechanical stiffening in this mode.
  • the beads serve both for stiffening and for feeding in the extinguishing sound, and the vibration damping takes place in exactly the significant vibration modes.
  • the sheet-metal element is provided with at least two corrugations running normally to one another, each of which carries a piezoactuator.
  • the component is provided with a central annular bead and at least four, preferably eight, of these radially outwardly extending beads, of which at least two each carry a piezoelectric actuator.
  • the ring bead mechanically counteracts the vibratory mode of buckling ("buckling mode"), and the radiating beads resist the bending and torsional modes, but by vectorically mixing the sound input of the piezoactuators to the radiating beads an acoustic cancellation can be achieved in all three modes. which reduces the number of required piezoactuators.
  • the piezoactuator is a flexible piezofilhe which follows the curvature of the bead snugly. As a result, a maximum efficiency of the introduction of force from the piezoactuators to the component can be achieved.
  • the piezoactuator has at least one pronounced piezostriction direction and is aligned parallel to the course of the bead.
  • the Striktionskraft of Piezoak- tuators thus acts exactly in Sick profile direction, whereby a maximum sound efficiency is achieved.
  • the piezoactuator can be glued to the component in a simple manner.
  • the preferred arrangement of the piezo actuator in the convex region of the bead thereby reduces the risk of detachment of the piezo actuator during operation.
  • Fig. 1 shows a component of the invention in plan view
  • Fig. 2 is a sectional view of the device taken along section line II-II of Fig. 1;
  • Fig. 3 is a fragmentary perspective view of one of the beads of the device of Fig. 1;
  • FIG. 4 shows a sectioned section through one of the beads of the component of FIG. 1 along a section line in the direction of the beading direction;
  • FIG. Figures 5 and 6 different variants of beads on components.
  • Fig. 7 shows a further device of the invention in the form of a Get ove r s tunnel for a motor vehicle in the Perspektivan ⁇ view.
  • a planar component 1 is shown in the form of a flat sheet metal panel.
  • the component 1 is provided for Verstei ⁇ tion with a central annular bead 2 and from this radially outwardly extending beads 3-6.
  • the beads 3 - 6 are arranged according to the fundamental modes of the component 1 tojosteifen this each against ei ⁇ nem fundamental mode, namely: the annular bead 2 for stiffening against the bulge mode, the longitudinal and transverse beads 3, 5 for stiffening the bending modes, and the diagonal beads 4, 6 for stiffening against the torsional modes.
  • the beads 3 - 5 are each equipped with a piezoactuator 7 - 9 for feeding structure-borne noise (vibration) into the component 1.
  • a structure-borne sound or vibration sensor 10 preferably a film-shaped piezoelectric transducer, is seated on the component 1 remote from the piezoactuators 7 - 9. The location of the vibration sensor 10 is chosen so that it is excited in each possible vibration mode of the device 1.
  • the piezoactuators 7 - 9 acted upon in such a manner with electrical signals that they produce by their piezoelectric effect of structure-borne noise and feed as Auslöschungsschall in the device 1, which compensates for the natural vibration of the device 1.
  • the controller receives a measurement signal from the vibration sensor 10 and follows the control target of minimizing this measurement signal.
  • the acoustic behavior of the device 1 can be modeled by a mesh of excitation points with acoustic point admittances Y 11 and mutual acoustic transfer admittances Y lk .
  • the fed into the device 1 acoustic power P is thus distributed
  • the piezoactuators 7-9 are arranged as follows.
  • Figs. 2 to 4 show - representative of all Piezoaktuatoren - the piezoelectric actuator 9 and its bead 5 in detail.
  • the piezoactuator 9 is preferably located at the location of the maximum convex curvature of the bead 5, wherein the curvature in the direction of the course 11 of the bead 5 is considered.
  • the bead 5 runs at each of its ends in a sequence of a convex portion 12, a turning point 13 and a concave portion 14 in the environmental plane of the device 1, and the piezoelectric actuator 9 is preferably in the convex portion 12 on the outside 15 of the bead fifth applied.
  • the radii Ri and R2 of the convex or concave curvature regions 12, 14 of the bead 5 are for example in the range of 20 to 2000 mm.
  • Each of the piezoactuators 7 - 9 may be of omnidirectional piezorestrictive type or - preferably - have a pronounced piezoelectric straightening direction 16, which is then preferably aligned parallel to the course 11 of the respective bead 3 - 5. As a result, the piezoactuators 7 - 9 generate tensile stresses over the curvature region 12, which can propagate exactly along the course of the bead 11.
  • one or more piezoactuators could - albeit with reduced acoustic efficiency or the risk of detachment - alternatively applied to a convex portion of the inside of a bead, in a concave portion on the inside or outside of a bead and / or transversely or obliquely to Sickenverlauf.
  • the piezoactuators 7 - 9 are in the form of a flexible piezoelectric film (piezo film), as e.g. from US 4,626,730 is known per se.
  • the piezoactuators 7 - 9 are glued to the beads 3 - 5 and closely conform to the curvature of the convex portion 12.
  • the length of the piezoactuators 7 - 9 in the direction of the skew curve 11 is tuned to the wavelength of the respective vibration mode to be damped, in particular in such a way that the length is not an integer divisor of the vibration mode in order to avoid the resonant excitation of harmonics ,
  • piezo actuators 3 - 5 are used, as required, to dampen the main or fundamental modes of the component 1.
  • the beads 3 and 5 are provided with piezo actuators, here the beads 3 and 5.
  • their drive signals, as well as vibration modes be compensated with intermediate directions, for example in the direction of the diagonal beads 4, 6, so that the illustrated third piezo actuator 8 could possibly be omitted.
  • the component 1 can basically be of any shape and material, as long as it allows the formation of beads.
  • FIGS. 5 and 6 show examples of non-planar components 1 in the form of a tube which carries an outwardly embossed bead 17 with a piezoactuator 18 or an inwardly embossed bead 19 with a piezoactuator 20.
  • the piezoactuators 18, 20 are respectively applied to the location of the maximum convex curvature of the bead 17 and 19, which is in Fig. 5, the central region of the bead 17 and in Fig. 6, the transition region of the bead 19 to the component. 1
  • FIG. 7 shows yet another embodiment of a highly irregularly shaped component 1, here a tunnel plate for a motor vehicle body comprising a web plate 21, on both sides subsequent apron plates 22 and end side end and heel plates 23.
  • a highly irregularly shaped component here a tunnel plate for a motor vehicle body comprising a web plate 21, on both sides subsequent apron plates 22 and end side end and heel plates 23.
  • longitudinal beads 24 - 26 For stiffening compared to the fundamental mode of longitudinal bending serve longitudinal beads 24 - 26, and for stiffening against the fundamental mode of buckling of the skirt plates are transverse beads 27 - 29th
  • the beads 24-29 are provided with piezoactuators 30-35, which each lie in the region of maximum convex bead curvature in the direction of the course of the bead.
  • Piezo converters 36, 37 at locations of maximum vibration amplitude decrease the control signal for the control of the piezoactuators 30-35. It is understood that the system presented here for active Vibrationdsdämpfung could be used in an analogous manner to an active sound generation in the device 1.
  • corrugations provided with the piezoactuator cushioning described herein can be fabricated with consistent mechanical strength with a smaller bead depth and a shorter bead exit than without cushioning, thereby resulting in manufacturing savings.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Prevention Devices (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Piezo-Electric Transducers For Audible Bands (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Abstract

L'invention concerne un élément de construction plat (1), notamment un élément en tôle, pourvu d'au moins un actionneur piézoélectrique (7 - 9) pour l'amortissement actif des vibrations de l'élément de construction, l'actionneur piézoélectrique étant disposé sur le côté intérieur ou le côté extérieur (15) d'une moulure (3 - 5) pratiquée dans l'élément de construction.
PCT/EP2010/052166 2009-02-19 2010-02-19 Élément de construction plat à amortissement des vibrations Ceased WO2010094786A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US13/201,985 US9366310B2 (en) 2009-02-19 2010-02-19 Planar component with vibration damping
DE112010000734.9T DE112010000734B4 (de) 2009-02-19 2010-02-19 Flächiges Bauelement mit Vibrationsdämpfung
CN201080008049.1A CN102317643B (zh) 2009-02-19 2010-02-19 具有振动阻尼的平面部件

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009009702 2009-02-19
DE102009009702.3 2009-02-19

Publications (2)

Publication Number Publication Date
WO2010094786A2 true WO2010094786A2 (fr) 2010-08-26
WO2010094786A3 WO2010094786A3 (fr) 2010-11-18

Family

ID=42340499

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/052166 Ceased WO2010094786A2 (fr) 2009-02-19 2010-02-19 Élément de construction plat à amortissement des vibrations

Country Status (4)

Country Link
US (1) US9366310B2 (fr)
CN (1) CN102317643B (fr)
DE (1) DE112010000734B4 (fr)
WO (1) WO2010094786A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9725154B2 (en) * 2014-05-13 2017-08-08 The Boeing Company Method and apparatus for reducing structural vibration and noise
JP7166865B2 (ja) * 2018-10-01 2022-11-08 株式会社ニューフレアテクノロジー 荷電粒子ビーム装置
DE102022129202A1 (de) * 2022-11-04 2024-05-08 Elringklinger Ag Verformungselement und Verwendung eines Verformungselementes und Baugruppe mit einem Verformungselement

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4626730A (en) 1984-08-14 1986-12-02 Massachusetts Institute Of Technology Method and apparatus for active control of vibrations
EP0720144A1 (fr) 1994-12-28 1996-07-03 FIAT AUTO S.p.A. Un système pour réduire le bruit dû aux vibrations dans un véhicule
WO1997016048A1 (fr) 1995-10-20 1997-05-01 C.R.F. Societa' Consortile Per Azioni Systeme de reproduction de sons destine a des vehicules

Family Cites Families (14)

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Publication number Priority date Publication date Assignee Title
US2620070A (en) * 1950-05-03 1952-12-02 Gen Tire & Rubber Co Washing machine tub and spin basket
DE3834853C2 (de) 1988-10-13 1999-12-02 Bayerische Motoren Werke Ag Anordnung zur Verminderung des Geräuschpegels im Innenraum eines Kraftfahrzeugs
US6138996A (en) * 1997-04-16 2000-10-31 Honda Giken Kogyo Kabushiki Kaisha Vibration control device for automotive panels
JP2002005228A (ja) 2000-06-22 2002-01-09 Honda Motor Co Ltd 車両の開閉用部材
US6375127B1 (en) * 2000-07-07 2002-04-23 Kari Appa Active control surface modal system for aircraft buffet and gust load alleviation and flutter suppression
US20020101135A1 (en) 2000-07-28 2002-08-01 Marco Giovanardi Method and device for noise damping
DE10042850A1 (de) 2000-08-30 2002-03-14 Hammerstein Gmbh C Rob Rückenlehne eines Kraftfahrzeugsitzes mit einem Rückenlehnenrahmen als Blechpressteil
US6600323B2 (en) 2001-08-24 2003-07-29 Trek, Inc. Sensor for non-contacting electrostatic detector
US7202588B2 (en) * 2003-12-03 2007-04-10 Honda Motor Co., Ltd. Chassis frame buckling control device and chassis frame deformation control device
US7510047B2 (en) * 2004-03-05 2009-03-31 Keiko Muto Speaker edge and resonator panel assembly
JP2006081637A (ja) 2004-09-15 2006-03-30 Star Micronics Co Ltd 洗濯機
JP2006118694A (ja) * 2004-09-21 2006-05-11 Nissan Motor Co Ltd 振動抑制装置の最適配置構成
DE102005044448B3 (de) 2005-09-09 2006-12-21 Universität Stuttgart Einrichtung zur aktiven und/oder passiven Schwingungsbeeinflussung eines transparenten, dünnwandigen Elements und deren Verwendung
US7360996B2 (en) * 2005-12-07 2008-04-22 General Electric Company Wind blade assembly and method for damping load or strain

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4626730A (en) 1984-08-14 1986-12-02 Massachusetts Institute Of Technology Method and apparatus for active control of vibrations
EP0720144A1 (fr) 1994-12-28 1996-07-03 FIAT AUTO S.p.A. Un système pour réduire le bruit dû aux vibrations dans un véhicule
WO1997016048A1 (fr) 1995-10-20 1997-05-01 C.R.F. Societa' Consortile Per Azioni Systeme de reproduction de sons destine a des vehicules

Also Published As

Publication number Publication date
WO2010094786A3 (fr) 2010-11-18
CN102317643B (zh) 2014-10-29
US20110298334A1 (en) 2011-12-08
DE112010000734A5 (de) 2012-11-15
CN102317643A (zh) 2012-01-11
DE112010000734B4 (de) 2019-03-28
US9366310B2 (en) 2016-06-14

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